Zero locking system for centrifugal apparatus



3 Sheets-Sheet 1 R. J. LACHAT ZERO LOCKING SYSTEM FOR CENTRIF'UGALAPPARATUS July 28, 1964 Filed Jan. 9, 1961 INVENTOR. REMY J* LACHATATTORNEYS R. J. LAcHAT 3,142,641 zERo LOCKING SYSTEM FOR CENTRIFUGALAPPARATUS July 28, 1964 5 Sheets-Sheet 2 Filed Jan. 9, 1961 INVENTOR.REMY J. LACHAT @y QL* ATTORN EYS 3,142,641 ZERO LOCKING SYSTEM FoRCENTRIFUGAL APPARATUS Filed Jan. 9, 1961 l R. J. LACHAT July 28, 1964 3Sheets-Sheet 3 l' |l h Il Ll INVENTOR. REMY J. LACHAT Y* ATTORNEYS wwwUnited States Patent O Filed Jan. 9, 1961, Ser. No. 81,571 7 Claims.(Cl. 21o-144) The present invention relates broadly to apparatus forcounterbalancing unsymmetrically distributed centrifugal forces in arotating body as exemplified by a substantially horizontal axis typelaundry drum, and is more particularly concerned with novel means forassuring that the counter-balancing system is accurately indexed priorto initiation of drum high speed rotation and before and after anybodily movements of the laundry appliance.

Various ways have been proposed to shorten the drying time of thewashing and drying cycles of a domestic laundry appliance as exemplifiedby an automatic washer or combination washer-dryer. One approach is toincrease the drying heat input to the dryer, however, this isdisadvantageous in View of the power requirements, as well as from thestandpoint of engineering design considerations which are requiredbecause of the increased power input to the drying means.

A second and preferred approach is to increase the rotative cylinderspeed used during the extraction part of the wash cycle, therebyremoving larger amounts of water from the load prior to the beginning ofthe tumble drying in the machine or line drying of the load. Thisaccomplishes a power consumption savings of the order of approximatelyeight to fteen times as compared with the high power input dryingprocess. However, it frequently occurs that when a load is introducedinto a laundry receiving cylinder or drum and the drum rotated atrelatively high speeds, the load distributes itself in such a mannerthat the center of mass of the loaded cylinder does not coincide withthe cylinder bearing axis. As a result, there is produced an unbalancedcentrifugal force which is directly proportional to the mass of theunbalanced portion of the total rotating mass, the square of the angularvelocity of such unbalanced mass, and to the radius of the unbalancedmass from the axis of rotation of the cylinder.

To overcome the unbalancing problem, it has been proposed to limit thespin speed of the horizontal axis type drum so that unbalanced loadsencountered during normal operation do not produce a suicient amount ofcentrifugal force to cause serious machine vibrations, which at timesmay be suicient to actually lift the machine frorn its supportingsurface and produce a violent movement colloquially referred to aswalking Other solutions to the problem which have been proposed includecontrol means which deactivates a spin mechanism in response to theexcessive motion in the apparatus, so that the drum or cylinderdecelerates to a tumbling speed for redistribution of the contentsthereof. Such an arrangement can readily be appreciated to bedisadvantageous since less liquid is centrifugally extracted from thecontents of the drum or cylinder than is desired, and in consequence, alonger drying period is required, whether or not machine or line-dryingis utilized.

There is also within the prior art disclosures suggestions of the use ofsuspension systems to suspend the entire laundry machine along with anadditional mass producing dead weight within an enclosing cabinet on acomplex spring system. Quite clearly when this approach is used there isrequired an enclosing cabinet of greatly increased size to allow for theviolent gyratory motions of such a system during operation of themachine or if the cabinet size is limited the machine drum or cylindermust be reduced in size to the extent that the drum capacity is toosmall to accomplish quality Washing and drying operations on normalloads.

In one construction wherein markedly improved results are obtained acasing is rigidly supported upon a base frame and a drum is mountedwithin the casing for rotation and vibratory movements relative to thebase frame. In such a machine, a plurality of liquid balancecompartments are disposed on the periphery of the drum, and thevibratory movements of the drum or cylinder are sensed by a movabledeflector member or by a movable iuid introduction nozzle to control theaddition of counterbalancing liquid to a particular liquid balancepocket or pockets.

The counterbalancing control means for such a machine must be indexed orcoordinated with respect to the pockets and their respective collectorsegments to assure addition of counterbalancing fluid to the properpocket or pockets during the counterbalancing of the drum at preciselythe correct time. Usually, any machine movements either by shipment fromthe factory or by change of location of the machine by the user havetended to destroy the original critical adjustment of either thepivoting deflector or the pivoting nozzle. The services of a technicianat the site of installation of the machine were then usually required,necessitating a partial dismantling of the machine in order to restorethe control means to a proper or zero indexed position.

In accordance with this invention there is provided what may be termed aself compensating or zero locking system, This zero locking systemfunctions to assure that whenever the drum is to be rotated at high spinspeeds, the correct dimensional relationship will always exist betweenthe balance fluid collector segments and the balance liuid deiiector orpivoting nozzle even if the machine is moved from one location toanother between machine operating cycles. This system desirably embodiespivotal stop means carried upon a common shaft with the deiector ornozzle, the stop means originally being adjusted to a zero position atthe factory or similar situs. The stop means in an illustrativeembodiment of this invention is normally contacted by a friction detentor brake member which is released when the access door to the drum isopened, or when other suitable release means is actuated. The frictiondetent is pivotally supported by casing structure, and when released,moves suiciently to restore the stop means to its original zero orindexed position. Closing of the access door or actuation of otherrelease means applies a braking or holding force to the friction detent,and thereby assures that when the counterbalancing action is initiated,the deiiector or nozzle is in its original zero or indexed position withrespect to the water balance pockets on the drum periphery.

It is accordingly an important 'aim of the present invention to provideimproved counterbalance control means for ia rotating receptacle.

Another object of the instant invention is to provide a balancing systemfor a laundry apparatus wherein the laundry liquid may be effective-lyutilized as a balancing fluid.

Still another object of this invention lies in the provision of abalancing system for `a rotatable receptacle provided with fluidreceiving counterbalancing pockets thereon, and wherein there isprovided means in control of the addition of fluid to the pockets toeffect counterbalancing, as well as means controlled by movements of theaccess door to the receptacle and interconnected between the receptaclemounting means and the fluid addition control means for automaticallyindexing Ithe control means with respect to the pockets tto assureaddition of counter-balancing fluid to the proper pockets during thecounte-rbalancing of the receptacle. v

A further object of the present invention is to provide an automaticallyself compensating indexing or zero locking system of the foregoingcharacter, which has utility with balancing systems of various types,and which is constructed of relatively few comparatively simple parts ofhigh reliability.

Other objects `and advantages of the invention will become more apparentduring the course of the following description, particularly when takenin connection with the accompanying drawings.

In the drawings, wherein like numerals designate like parts throughoutthe same:

FIGURE l is a side elevational View, with parts removed yand with partstaken in section, to more clearly illustrate the self compensatingindexing or zero locking system of this invention;

FIGURE 2 is a rear elevational view from which parts have been removedto show in further detail a laundry machine embodying the control meansand indexing means of this invention;

FIGURE 3 is an enlarged elevational view of the control and indexingstructure;

FIGURE 4 is an enlarged elevational View, with parts thereof taken insection and with other parts eliminated, showing more fully the lockingsystem as it appears in FIGURE l;

FIGURE 5 is a bottom plan view of the friction detent and release meanstherefor constituting a part of the control means and indexing meansherein provided',

FIGURE 6 is a detail view of the access door hinge structure and thebrake release structure associated therewith;

FIGURE 7 is a sectional View, with parts thereof in elevation,illustrating further details of the access door latch means and the camand cable structure employed in connection therewith; and

FIGURE 8 is a sectional view taken along the line VIII-VIII of FIGURE 2with some parts eliminated to more clearly show a second embodimentincorporating a pivoting nozzle.

Referring now iirst to FIGURES l and 2, there is shown and designatedgenerally by the numeral 1t? a domestic laundry appliance which may takethe form of a so-called combination washer-dryer. Certain structuralportions of the laundry appliance have been omitted in the interest ofclarity of illustration and since such portions are not essential to thepresent invention.

In the exemplary structural organization shown, the machine 10 isprovided with a base plate or support structure indicated at 11. Theexterior cabinet members are mounted on the support structure 11 to forma complete aesthetically appealing enclosure for the machine 10. Thefront wall provides access such -as at 12 by means of which a batch ofmaterials to be laundered may be placed in or withdrawn from a treatmentzone formed within the machine 10.

The support structure 11 is supported upon front and rear legs 13 and14, and upon the base portion there is lixedly but resiliently mounted asupporting structure or pylon member designated at 15, and which maytake the form of a pair of spaced uprights 15a and 15b having a crossmember 21. The base portion of the cabinet 11 further ixedly supports acasing 16 spaced within the enclosure cabinet, and shaped along itslower portion as indicated in FIGURE 2 to provide a sump 16a.

Mounted for rotation within the casing 16 and for vibratory movementrelative to the supporting structure 11 and casing 16 is a perforateddrum or cylinder I7 having a passaged front wall 17a and closed rearwall 1'7b connecting generally centrally thereof with shaft means 18received at its opposite end in xed bearing means 19 encased in abearing Ahousing 2t). The bearing housing 2t) is attached in anysuitable manner to the generally horizontal pylon cross member 21connected at its opposite ends to the upright members 15a and 15b, andconstituting the herein provided means for mounting the drum 17 forrotation within the casing 16 and for vibratory movement relative to thecasing 16 and support structure 11. As will be later described infurther detail, rotation of the drum 17 with an unbalanced load thereincauses the pylori member 21 to vibrate in opposed horizontal directionsas indicated by the arrows 22, and in the absence of the application ofcounterbalancing forces, such vibration may be suiicient to cause themachine 10 to actually walk upon the floor. This situation can existwhether or not a supporting structure of the character indicated at 15is employed, and it can accordingly be appreciated that the supportingmeans 15 can take the form of :an A-frame or other basket or drummounting arrangements,

The drum or basket 17 is further provided with recess means at aplurality of circumferentially spaced points on its periphery' toaccommodate mounting in such recesses a liquid balancing receptacle, ofwhich three are provided in the illustrative embodiment shown anddesignated therein by the numerals 23a-c. Each balancing receptacle isof essentially identical construction and comprises a generallytrough-shaped tray member having a wall 2d spaced radially outwardly ofan imperforate wall portion 25 formed on the drum 17 at the recessedarea. Each receptacle 23a-c further includes side walls 26, and in thegenerally diagrammatic showing of FIGURE l, front and rear walls 27 and28.

Illustratively, the receptacles 23a-c and injection intake structuretherefor may be constructed in the mam ner indicated in FIGURES l and 2.The rear Wall 28 of each receptacle 23 and rear wall 17h of the drum 17may be passaged to receive a connector member 29 in lluid receivingcommunication with an inlet assembly generally designated by the numeral32 having an inner diameter 32d, and desirably provided by a generallyU-shaped ring member divided as at 33 to provide three inlet segments32a-c extending through 120 of arc on the rear wall 17b ofthe drum 17.

The drum 17 is rotatably driven within the casing 16 1n any desiredmanner, and illustratively there may be provided motor means 39 providedwith a shaft 40 mounting pulley means 41 about which is trained a belt42 also wrapping a pulley 43 on the drum drive shaft 18. Desirably themotor means 39 connects with transmission means having low and highspeed capabilities, and shifting or clutching means preferably form apart of the transmission means in order that continued acceleration ofthe basket or drum 17 can be terminated during counter-balancing. This,however, forms no part of the instant invention and the details thereofare accordingly not illustrated.

FIGURES 1 and 2 show a first embodiment of a water or fluid balancesystem used with this self compensating or indexing zero locking systemwhich incorporates a pivoting detlector. In this system a nozzleassembly 45 having a nozzle outlet 45a is firmly mounted in the rearwall 16h of the casing 16 and is targeted or directed to deliver astream of balancing Huid to the collector segments 32a-c on the rearwall 17 b of the drum 17 Whenever this stream is not interrupted. Apivoting control member 46, which pivots as a result of vibrations ordeiiections of the drum 17 and pylon cross member 21 due to the spinningof an unbalanced load in the drum 17, includes an enlarged end portion46a. This end portion when in its neutral position will interrupt thestream of balancing fluid emanating from the nozzle outlet 45a anddeflect it back into the sump 16a from Where a pump (not shown) willreturn the uid back to the nozzle assembly 45 during the extraction ofhigh speed spin cycle.

During the extraction cycle with an unbalanced load present, the controlmember 46 will pivot, as later eX- plained in detail, up and down withdeflections of the pylon cross member 21 such that when deliections ofthe cross member 21 are to the left of the vertical centerline as shownin FIGURE 2 the control member 46 will move upwardly to move end portion46a above the fluid stream emanating from the nozzle outlet 45a andallow this fluid to pass into the proper inlet segment or segments fromwhere it will pass into the proper balance pocket or pockets tocounterbalance the unbalanced load, causing the forced oscillation ofcross member 21.

FIGURE 8 shows a second embodiment of a iiuid balance system verysimilar to the rst embodiment of FIG- URES l and 2 except that in thisembodiment the nozzle assembly 45 is iirmly mounted in the end portion46a of the control member 46. A predetermined deflection to the left ofthe pylon cross member 21 will allow the end portion 46a to carry thenozzle outlet 45a so that the balancing uid will pass over the top ofthe inner diameter 32d of the collector segments and into the propercollector segment or segments for delivery to the proper balance pocketor pockets. Clearance is provided in the rear Wall 1612 of the casing 16to allow for the movements of the nozzle assembly 45. Both embodimentsrespond identically to the deflections of the drum and pylon crossmember.

For either of the fluid balance system embodiments to function properly,it is vitally important that precise relationships exist at all timesbetween the deilections of the drum 17 and pylon cross member 21 and thepivotal movement of the control member 46. Adjustment of the controlmember 46 must be such that in the iirst embodiment, that is, thepivoting deilector or interrupter system, the end portion 46a of thecontrol member 46 will move upward out of the path of the balancingfluid emanating from the nozzle outlet 45a at a predetermined deflectionor amplitude of vibration of the drum and pylon cross member to the leftof the machine vertical centerline. This illustrative adjustment, whichwas determined and veriiied under test conditions, will allow thebalancing uid to enter the proper balance pocket or pockets tocounterbalance the unbalanced load producing the deflections while usinga minimum volume of balancing uid. The adjustment for the secondembodiment, that is, the pivoting nozzle uid balance system, is the sameas for the rst embodiment except that in this case the end portion 46amust lift the iiuid stream emanating from the pivoting nozzle outlet 45aabove the inner diameter 32d of the collector segments 32a-c at theprecise predetermined amplitude of vibration to the left of the verticalcenterline of the machine of the drum and pylon cross member.

The aforementioned adjustment is so important that if means are notbuilt into the machine to assure this proper adjustment at all times,the fluid balance system may become much less effective or evencompeltely inoperative when this adjustment is upset either by movingthe machine or by a poor original adjustment,

Such problems are herein effectively eliminated by the provision of azero locking system embodying means controlled by movements of theaccess door 12 and interconnected between the casing rear wall 16h andcon trol member 46 for automatically indexing the control means to theproper adjustment with respect to the inner diameter 32d of thecollector segments 32a-c to assure addition of counterbalancing uid tothe proper balance pockets during the counterbalancing of the receptacle17.

The zero locking system of this invention is designated generally in thedrawings (FIGURES 1 and 2) by the legend S, and may be seen to comprisea generally channel-shaped bracket member 5t) having outwardly turnedange portions 51 (FIGURE 3) secured by a fastening means 52 to a wallportion 21a of the `plyon cross member 21. The pylon cross member 21 maybe seen to be further formed with upright wall portions 2lb and 21C, thelater wall portion extending a relatively short distance downwardlybetween casing rear Wall 1Gb and rear Evallstla of the generallychannel-shaped bracket mem- The bracket member 5t) is shaped to provideoutwardly extending wall portions 50b and 50c, and secured to the rearwall 50a of this bracket member by adjustable fastening means 53 is agenerally U-shaped plate member 54. The plate member 54 is formed with arelatively flat wall portion 54a lyng flush against the bracket memberrear wall 50a, and the plate member rear wall 54a is slotted at 55 toreceive the fastening means 53 for a purpose to be shortly described.The plate member 54 is further constituted by a pair of spaced wallportions 5412 and 54C extending outwardly at generally right angles tothe rear wall portion 54a, and the end walls 54h and 54C are aperturedto receive control member 46 adjusting means 56, the purpose of whichwill also shortly be described.

The control member 46 is nonrotatably carried upon shaft means 57extending through an apertured embossment 5S formed in the rear wall 16hof the casing 16. The shaft means 57 may be observed to be provided witha stepped outer diameter, and this shaft is mounted for rotation in acollar member 5g having a ange portion 59a thereon bearing against thefront surface of the rear wall 50a of the bracket means 56. The flange59a of the collar member 59 is securely attached by any convenientmethod to the rear wall Sila of the bracket member 5t). The opposite endof the collar member 59 forms a thrust bearing surface for the bodyportion 60a of stop or driven means 66, and it is to be noted that thestop means 60 is connected to the shaft 57 by fastening means 61 whichmay take the form of a screw threadably received in the shaft 57.

The body portion 60a of the stop means 60 is of generally flatconfiguration and extending forwardly from the body portion is a pair ofspaced ear portions 60h and 60e, the latter ear portion being in contactwith the end wall 54e of the plate member 54 when the control member 46is in a zero indexed or neutral position with respect to the balancingreceptacles 23 and their collector segments. It may accordingly beobserved at this point that positioning of the plate member 54 throughthe adjusting means 56 and locking means 53 determines the properposition or adjustment of the control member 46, with regard to theinner diameter 32d of the collector segments.

The stop member 60 is maintained in abutment with the plate member 54after the original zero adjustment, and returned to abutting contacttherewith during swinging of the deflector member 46 by provision ofspring means 62 connected to the body portion of the stop member 60 andto the end wall Stb of the bracket member 50. As a further structuralfeature of the stop member 6) the body portion 66a thereof is downwardlyextended to provide an end portion 60d against which bears a rearwardlyextending lange portion 63a formed on a tab por-tion 63b of a levermember 63.

The lever member 63 is pivotally connected at 64 to a more or lesschannel-shaped bracket member 65 (FIG- URE 5) having a wall portion 65awelded or otherwise secured to the casing rear wall 1617 which in turnis rigidly connected to base plate 11. Spring means 66 connected betweenthe lever member tab portion 63b and the end wall Stic on the bracketmember 50 resiliently automatically takes up any lost motion betweenmembers 60 and 63 by maintaining the lever member 63 in abutting contactwith the end portion 66d on the stop member 60. As will be more fullynoted later, the spring force applied by the spring means 62 is greaterthan the force of the spring means 66, so that the stop member 60 isreturned to abutting contact with the plate member 54,

27 thereby automatically maintaining the indexed position of thedeflector member 46.

The lever member 63 is shaped to provide an extended main body portion63C, and one end of the body portion of the lever member is elampinglyengaged during the entire high spin speed extraction cycle by a brake orfriction detent means generally designated by the numeral 67. Thefriction detent means 67 may be provided by 0pposed friction shoemembers 67a and 6711, the friction shoe member 67a being stationarilymounted by a wall portion 65h formed on the bracket means 65. Thefriction shoe member 67b, on the other hand, is movably carried by legportion 63a of a lever arm 63 pivotally supported at 69 upon a tabportion 70 forming a part of or attached to wall portion 65e of thebracket member 65. The means attaching the brake or shoe member 67h tothe lever leg portion 68a may of course take various forms, andillustratively the fastening means 71 may be a cotter pin.

As appears in FIGURE 5, the lever arm 68 is shaped to provide a secondleg portion 68h and connected to one side of this leg portion is firs-tspring means 72, also attached to Wall portion 65d on the more or lesschannel-shaped bracket means 65. The lever arm leg portion 6817 furtherhas attached thereto second sring means 73 connected at its opposite endto a coupling member 74. As will be later described, the first springmeans 72 is effective when the tension in cable 75 is reduced by openingaccess door 12 so as to allow lever arm 68y to swing clockwise as shownin FIGURE to release the brake means 67, thereby permitting the leverarm 63 to pivot about its connection 64 to the bracket means 65, so thatthe spring means 62 can always restore the stop member 60 and connectingcontrol member 46 to a zero or properly pre-adjusted indexed positionwith respect to the inner diameter 32d of the collector segments. Thesecond spring means 73, on the other hand, functions to take up slack incable means 75 connected to the access door hinge in a manner to belater fully described. Accordingly, the spring means 73 normally ischaracterized by a relatively greater spring force than the spring means72.

The cable means 75 is shown in FIGURE 5 as connected to the couplingmember 74, and substantially entirely along its length the cable 75 isreceived in a stationary conduit 76. The conduit 76 extends along thecasing rear wall 16b and along casing side wall 16e (FIG- URE l) to thecasing front wall 16a, and along said wall to the access door hinge. Ofcourse, the path taken by the conduit 76 may be dilferent from thatindicated, however, in the illustrative embodiment shown, the conduit 76is supported by the casing structure by grommets or the like 77 (FIGURE5) attached by fastening means 78 to bracket means 79 suitably attachedto the casing walls or other appropriate structure.

The access door 12 in FIGURE l is indicated as of the vertically openingtype, however, the instant invention is of course of equal utility witha horizontal opening type door. Referring now to FIGURES 6 and 7, thecable means 75 is connected to a cam follower lever member 80 mounted bya shaft member 81 received at opposite ends in wall portions 82a and 82bof bracket means 82, which may be formed as a part of the casing frontwall structure or may be a separate member welded or otherwise attachedthereto.

The access door 12 is supported from two of the bracket means 82. It isnecessary that only one of the bracket means 82 contain the cam followerlever member 8). The bottom wall 82C of the bracket 82 is pierced toprovide a tab 82d to anchor the end of the cable guide conduit 76 as bymeans of the grommet 77 and fastening means.

Each of the two mounting brackets 82 also mount access door hinge means86 on shaft means extending between bracket end or side walls 82a and82h. When the door is in the closed position, the outside aestheticsurface E of the door lies in the plane of the frontaesthetic panel ofthe machine which extends upwardly from the support structure 11 aspreviously explained. The hinge means S6 further includes a cam portion86a which serves to drive the cam member Si) about the pin 81 againstVthe bias of spring 72 when the access door 12 is closed.

As was indicated hereinabove, the control member 46 is originallyadjusted to a zero or indexed position with respect to the collectorsegments 32a-c and the balancing pockets 23 when the brake or frictiondetent 67 is released by utilization of the adjusting means 56connecting with the plate member 54 and bracket member 50. Once thedesired position of control member 46 relative to collector segments32a-c is established by threadable movement of the adjusting means 56,the locking means 53 is tightened. Accordingly, when so adjusted thestop member 60 and particularly the wall portion 60e thereof is inabutting contact with the wall portion 54C on the plate member 54, andis resiliently held or maintained in this position by the spring means62, the spring action being abetted by the weight of the detlector arm46.

Opening of the access door 12 for the insertion or removal of thefabrics to be laundered causes swinging action of the hinge means 86from the full line to dotted line position in FIGURE 6, and by action ofthe spring means 72 (FIGURE 5) the cam follower lever member 80 isshifted by the cable 75 from the full line to dotted line position ofFIGURE 6, The spring means 72 at the same time exerts sufficient springforce on the lever arm leg portion 68h to pivot the lever arm 68 aboutthe point 69, releasing the holding or braking force of the brake ordetent means 67b. This permits the lever member 63 to be pivoted aboutthe point 64 by the spring 62, and since the spring force of the springmeans 62 is greater than the force exerted by the spring means 66, thestop member 60 is drawn or pivoted clockwise by the spring means 62 tobring the surfaces 60C and 54C again into abutting engagement.Engagement of these surfaces assures that the control member 46 is againin its zero or indexed position.

Closing of the access door for initiation of the laundering cycleessentially reverses the action described, and the cam surface 86a onthe hinge means 86 forces the cam follower lever member 86 to rotate ashort distance counterclockwise, exerting a force on the cable 75 topivot the lever arm 68 to again engage the brake members 67a and 67hagainst the body portion 63C of the lever arm 63.

The spring means 66 (FIGURE 3) maintains the lever member flange portion63a against the end portion 60d of the stop means 60, however, the stopmember 60 and connecting control member 46 are free to pivot duringperformance of the counterbalancing function.

The reason for the necessity of a self compensating indexing or zerolocking system can best be understood by making reference to theoperation of the balance system and the relative movements between thestationary and moving parts during the balance operation. This will beexplained in conjunction with the first embodiment incorporating thepivoting deflector balance system as shown in FIGURES 1 and 2, but itshould be understood that the operation is generally the same for thesecond embodiment incorporating the pivoting nozzle balance system ofFIGURE 8. In the explanation the assumption will be made that there is anegligible difference in the phase anglevbetween the unbalanced portionof the load and the de'ection it produces or stated in another way, asthe unbalanced load passes the horizontal centerline through the drumshaft the deection of the pylon cross member 21 will be at a maximumdistance from the vertical centerline of the machine on the same side ofthe vertical centerline as the unbalanced load.

Referring to FIGURE 2, it can be seen that as the unbalanced load M inthe drum 17 is spun at a high extraction speed there will be adeflection of the drum 17 and pylon cross member 2l. When rotating inthe direction indicated (clockwise in the rear elevation of FIGURE 2),the unbalanced load M will cause the pylon cross member 21 to begin todeilect to the left of the machine vertical centerline at the instant itcrosses the vertical centerline beneath the horizontal centerline. Aftera predetermined amplitude of vibration or deflection of the pylon crossmember 21 to the left, it is desirable to have injection of thebalancing tluid into the inlet segments begin. With the properaforementioned adjustment of the control member 46 with respect to theinner diameter 32d of the collector segments, the injection will beginat this time. Injection occurs at this time since the movement of thepylon cross member 21 causes the wall portion 54C of the plate member todrive the stop member 69, because of the resistance imparted by thestationary tab 63a, counterclockwise about the pivot 57 to the pointwhere the end portion 46a rises enough to allow the balancing fluidemanating from the nozzle outlet 45a to enter the proper collectorsegment or segments from Where it enters the proper balance pocket orpockets to eticiently counterbalance the unbalanced load M.

As the unbalanced load M continues upward toward the horizontalcenterline, deilection of the pylon cross member 21 to the leftincreases and injection continues. At the instant the unbalanced load Mcrosses the horizontal centerline in an upward direction, the deectionof the pylon cross member 21 to the left is at a maximum. As theunbalanced load continues upward toward the upper portion of thevertical centerline, the pylon cross member deflection will be to theright toward the neutral position and at some predetermined angle of theunbalanced load before it reaches the vertical centerline the endportion 46a of the control member 46 in its downward motion will againinterrupt the ow from the nozzle outlet 45a and deect it back into thesump 16a to thus end injection.

As the unbalanced load M crosses the vertical centerline as shown inFIGURE 2, the pylon cross member 21 will be in its neutral position andthe control member 46 will be in its zero or adjusted position. Duringthe next 90 of rotation of the unbalanced load the deflection of thepylon cross member continues to the right, but there will be noinjection. Injection is precluded since when the pylon cross member 21deflects to the right of the vertical centerline, the stop member 60breaks contact with the stationary drive tab 63a of the lever member 63and thus the control member 46 remains in its neutral position wheneverthe pylon cross member deects -to the right of the vertical centerline.

When the unbalanced load M passes the horizontal centerline in itsdownward movement, the deection of the pylon cross member 21 to theright will be at a maximum and the deection will again start to theleft. At the point when the unbalanced load M again crosses the lowerportion of the vertical centerline, the stop member 66 will againcon-tact the tab portion 63a of the lever member to allow the controlmember 46 to be pivo-ted as dellection of the pylon member to the leftcontinues.

IGURE 2 shows that since the end portion 46a of the .Control member 46is much further from the pivot point 57 than the point on the stopmember 60 that is contacted by the wall portion 54C, there will be anamplification at the end portion 46a of the pylon cross memberdeflections. For this illustrative structure the amplification isapproximately 16 to l. Thus if the pylon cross member 21 had a maximumdeection of .050 of an inch to the left of the vertical centerline, theend portion 46a of the control member 46 would rise .800 of an inch.

If an automatic indexing or zero locking system were not provided tomaintain a constant immovable relationship between the tab portion 63aof the lever member 63 and the stop member 60 and the machine werebodily moved, the critical adjustment of the control member 46 would beimpaired. This happens because in the bodily shifting or movement of themachine the base plate or support structure 11 may assume a somewhatdifferent l@ angle in its new position and produce a change in angularrelationship between base plate 11 and pylon structure 15. In such acase while casing 16 will keep its same angular position with respect tothe support structure 11, the drum 17 and pylon cross member 21 beingsupported semi-rigidly from the pylon legs 15a and 15b^may shift withrespect to the casing 16 and base plate 11. This small lateral shift ofthe pylon cross member 21 will be amplified at the end portion 46a ofthe control member 46 by a factor of 16 in the illustrative machine. Theend portion 46a in its new neutral position will be out of preciseadjustment with respect to the inner diameter 32d of the collectorsegments 32a-c. This will impair or destroy the proper coordinationbetween the deflection of lthe pylon cross member and fluid injectionthereby making the balance system much less efficient or eveninoperative.

The zero locking system eliminates this serious misadjustmentpossibility. With this system, the machine can be bodily moved fromposition to position with no concern for the original critical balancingadjustment since the zero locking system of this invention will alwaysassure the original precise adjustment. This is true since whenever themachine is to be used in its new position, it will be necessary to openthe door and place a clothes load in the drum 17. As explained earlier,the opening of the door 12 will release the brake or friction detentmeans 67 and allow the lever member 63 and the control member 46 to bepivoted by action of the spring 62 until the stop member 60 againcontacts the wall portion 54e` and lost motion is eliminated betweenmembers 60 and 63 thereby assuring the proper adjustment. It should bepointed out that when the machine is moved and even with the zerolocking system there will be a very minute dimensional change in theVertical relationship between the end portion 46a and the inner diameter32d of the collector segments. This slight change will be the actualmovement that takes place between the pylon and the casing and will notbe amplified 16 times as previously explained. This slight change willnot effect the balancing operation.

Although the zero locking system as explained is operated by the accessdoor 12, it would also be possible to have the cable 75 operated by anelectric or air solenoid forming a part of a manual or automaticcontrol. It would only be necessary at sometime in the machine cycleprior to the extraction or high speed portion to energize the electricor air solenoid to release the brake 67 and allow the lever member 63and control member 46 to be returned by the spring 62 to their zeroposition and then subsequently to deenergize the electric or airsolenoid to relock the brake means.

The embodiments of the invention in which an exclusive property orprivilege is claimed are defined as follows:

1. Counterbalancing apparatus, comprising a rotatable receptacle,

stationary support means,

a cabinet enclosing said stationary supporting means and saidreceptacle,

mounting means mounting said receptacle on said stationary supportingmeans for rotative and vibratory movements relative thereto,

a door in said cabinet controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle forreceiving counterbalancing fluid in response to vibratory movements ofsaid receptacle,

means including control means for adding uid to said pockets to eiectthe counterbalancing of said receptacle during rotation of unbalancedloads within said receptacle,

indexing means interconnected between said mounting means and saidcontrol means for automatically indexing said control means with respectto said pockets to assure addition of said counterbalancing fluid to theproper pockets during the counterbalancing of said receptacle, and

connecting means between said door and said indexing means to preindexthe control means Whenever the door is actuated.

2. Counterbalancing apparatus, comprising a rotatable receptacle,

stationary supporting means,

a cabinet enclosing said stationary supporting means and saidreceptacle,

mounting means mounting said receptacle on said stationary supportingmeans for rotative and vibratory movements relative thereto,

a door in said cabinet controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle forreceiving counterbalancing fluid,

control means including a nozzle member and a detlector member movablerelative to said nozzle member controlling the addition of fluid to saidpockets to effect the counterbalancing of said receptacle duringrotation of unbalanced loads within said receptacle,

and indexing means interconnected between said mounting means and saiddellector member for automatically indexing said deliector member Withrespect to said pockets to assure addition of said counterbalancingiluid to the proper pockets during the counterbalancing of saidreceptacle,

connecting means connected to said indexing means and having anoperative connection with said door to preindex the control meansWhenever the door is actuated.

3. Counterbalancing apparatus, comprising a rotatable receptacle,

stationary supporting means,

a casing,

mounting means mounting said receptacle on said supporting means forrotation Within said casing and vibratory movements relative to saidsupporting means,

a door supported by said casing controlling access to said receptacle,

a plurality of Huid-receiving pockets mounted on said receptacle forreceiving counterbalancing fluid in response to vibratory movements otsaid receptacle,

means for directing fluid into said pockets to effect a counterbalancingof unbalanced loads in said receptacle,

detlector means pivotally supported by said mounting means and movableWith respect to said directing means to control the addition of fluid tosaid pockets,

means limiting the movement of said deflector means to position saiddellector means in duid-blocking relation to said directing means whenthe amplitudes of the vibrations do not exceed a predetermined level,

lever means pivotally mounted by said casing and engageable with saidlimiting means,

locking means connected to said lever means, and means connecting saiddoor and` said locking means to maintain said lever means in astationary position relative to said casing when said door is closed andreleasing said lever means when said door is open to return saiddeilector means to blocking relation relative to said directing meansand indexed with respect to said pockets to assure addition of saidcounterbalancing uid to the proper pockets during the counterbalancingof said receptacle.

4. Counterbalancing apparatus of the character delined in claim 3 inwhich t2 t t resilient means connects to said limiting means to returnsaid deflector means to an indexed position, and in which resilientmeans urges said lever means against said limiting means. 5.Counterbalancing means of the character deined in claim 3, in whichreceptacle,

stationary supporting means,

a casing,

mounting means mounting said receptacle for rotation within said casingand vibratory movements relative to said supporting means,

a door supported by said casing controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle forreceiving counterbalancing duid in response to vibratory movements ofsaid receptacle,

means for directing fluid into said pockets to effect a counterbalancingof unbalanced loads in said receptacle,

control means pivotally supported by said mounting means to control theaddition of tluid to said pockets,

means limiting the movement of said control means to block uid llow tosaid pockets when the amplitudes ofthe vibrations do not exceed apredetermined level,

lever means pivotally mounted by said casing and engageable with saidlimiting means,

locking means connected to said lever means, and means connecting saiddoor and said locking means to maintain said lever means in a stationaryposition relative to said casing when said door is closed and releasingsaid lever means when said door is open to return said control means tosaid blocking position and indexed with respect to said pockets toassure addition of said counterbalancing duid to the proper pocketsduring tlie counterbalancing of said receptacle.

7. Counterbalancing apparatus comprising a rotatable receptacle,

stationary supporting means,

a casing,

mounting means mounting said receptacle for rotation Within said casingand vibratory movements relative to said supporting means,

a door supported by said casing controlling access to said receptacle,

a plurality of fluid-receiving pockets mounted on said receptacle forreceiving counterbalancing fluid in response to vibratory movements ofsaid receptacle,

means for directing fluid into said pockets to effect a counterbalancingof unbalanced loads in said receptacle,

control means pivotally supported by said mounting means,

said directing means mounted on said control means and movable with saidcontrol means to control the addition of uid to said pockets,

means limiting the movement of said control means to block duid ow fromsaid directing means to said pockets when the amplitudes of thevibrations do not exceed a predetermined level,

lever means pivotally mounted by said casing and er1- gageable with saidlimiting means,

locking means connected to said lever means, and

eans connecting said door and said locking means to maintain said levermeans in a stationary position relative to said casing when said door isclosed and releasing said lever means when said door is open to returnsaid control means to said blocking position and indexed with respect tosaid pockets to assure addition of said counterbalancing fluid to theproper pockets during the counterbalancing of said receptacle.

References Cited in the le of this patent UNITED STATES PATENTSArmstrong Sept. 13, 1955 De Moss Aug. 28, 1956 Burkall Oct. 30, 1962Scott et al. Mar. 5, 1963

1. COUNTERBALANCING APPARATUS COMPRISING A ROTATABLE RECEPTACLE,STATIONARY SUPPORT MEANS, A CABINET ENCLOSING SAID STATIONARY SUPPORTINGMEANS AND SAID RECEPTABLE, MOUNTING MEANS MOUNTING SAID RECEPTACLE ONSAID STATIONARY SUPPORTING MEANS FOR ROTATIVE AND VIBRATORY MOVEMENTSRELATIVE THERETO, A DOOR IN SAID CABINET CONTROLLING ACCESS TO SAIDRECEPTACLE, A PLURALITY OF FLUID-RECEIVING POCKETS MOUNTED ON SAIDRECEPTACLE FOR RECEIVING COUNTERBALANCING FLUID IN RESPONSE TO VIBRATORYMOVEMENTS OF SAID RECEPTACLE, MEANS INCLUDING CONTROL MEANS FOR ADDINGFLUID TO SAID POCKETS TO EFFECT THE COUNTERBALANCING OF SAID RECEPTACLEDURING ROTATION OF UNBALANCED LOADS WITHIN SAID RECEPTACLE, INDEXINGMEANS INTERCONNECTED BETWEEN SAID MOUNTING MEANS AND SAID CONTROL MEANSWITH RESPECT TO SAID POCKETS TO ASSURE ADDITION OF SAID COUNTERBALANCINGFLUID TO THE PROPER POCKETS DURING THE COUNTERBALANCING OF SAIDRECEPTACLE, AND CONNECTING MEANS BETWEEN SAID DOOR AND SAID INDEXINGMEANS TO PREINDEX THE CONTROL MEANS WHENEVER THE DOOR IS ACTUATED.